Double-twisting device for textile yarns



P. MAURIN DOUBLE-TWISTING DEVICE FOR TEXTILE YARNS Jan. 10, 1967 Filed May 25, 1964 2 Sheets-Sheet 1 Jan. 10, 1967 P. MAURIN 3,295,737

DOUBLE-TWISTING DEVICE FOR TEXTILE YARNS Filed May 25, 1964 2 Sheets-Sheet 2 I n-a l M i United States Patent 3,296,787 DUUBLE-TWIS'HNG DEVllCE FOR TEXTILE YARNS Paul Maui-in, 44 Rue Lafayette, Onlliins, France Filed May 25, 1964, Ser. No. 369,920 Claims priority, application France, .ian. 28, 1964, 936,121 14 Claims. (Ci. 57-5831) This invention relates to a double-twisting device for textile yarns, of the kind wherein an axially bored spindle, having one end rotatably mounted in a frame, has a bobbin holder freely rotatably mounted on its other end and also bears a casing, which is secured to an intermediate part of the spindle and which has a radial yarn passage communicating with the axial aperture in the spindle, the device also comprising means for preventing the bobbin holder from rotating relatively to the frame.

In a first known double-twisting device of the kind specified, the means for preventing the bobbing holder from rotating relatively to the frame comprise an unbalance weight which is secured near to the periphery of the bobbin holder. Such means do not require mechanical power in order to operate but do not provide a positive connection between the bobbing holder and frame. Consequently, the bobbin holder may be rotated if an external force is applied to it which is greater than the couple produced by the unbalance weight. In theory, the resistive couple due to the unbalance Weight could be increased, but in practice any increase in the weight of this item would upset satisfactory operations of the device.

In a second known kind of double-twisting device of the kind specified, the connection between the bobbin holder and the frame is by magnetic means, one element of which is rigidly secured to the bobbin holder and is disposed inside the balloon formed by the yarn, while the other element is rigidly secured to a stationary holder disposed outside the yarn balloon. As in the previous case, no positive connection is provided, and the disadvantages are the same as in the previous case.

In a third known kind of double-twisting device of the kind specified, the connection between the bobbin holder and the frame is provided by rotating system adapted to rotate around an axis different from the spindle axis. Devices of this kind provide a positive connection between the bobbin holder and the frame and therefore ensure that there is no chance of the bobbin being rotated, However, they cause considerable friction and therefore tend to reduce the efficiency of the machine, particularly since the spindle runs at very high speed.

It is an object of the invention to provide a doubletwisting device of the kind specified which is free from the disadvantages hereinbefore recited. To this end, according to the invention there is provided a double-twisting device for textile yarns, of the kind wherein an axially bored spindle, having one end rotatably mounted in a frame, carries a bobbin holder freely rotatably mounted thereon at its opposite end, and a casing which is secured to an intermediate part of the spindle, the casing being provided with a radial yarn passage communicating with the axial aperture in the spindle, including means for preventing the bobbin holder from rotating with respect to the frame comprising a relatively small unbalance weight associated with the bobbin holder and rotary mechanical connecting means associated with the bobbin holder and the frame and rotatable about an axis other than the axis of rotation of the spindle.

This special combination ensures, in a reliable and positive fashion, that the bobbin holder is maintained stationary by the mechanical system when the machine is started and in the event of any disturbance in the unwinding of the reeli.e., in cases in which the unbalance 3,296,787 Patented Jan. to, 1967 weight systems would fail to operate satisfactorily. In normal operation, however, the unbalance weight can maintain the bobbin stable on its own, so that the mechanical system rotates idly, with the result that driving power is reduced, efficiency improved and wear reduced. In other words, the bobbin is stabilized when running by a very small unbalance weight and the mechanical stabilizing system operates only as a safety feature, at starting, in the case of disturbances in unwinding and at stopping the spindle.

The rotating mechanical system connecting the bobbin holder to the frame may comprise a first disc and a second disc which extend around a spindle for the bobbin with considerable clearance therebetween, the first disc being mounted in the bobbin holder and the second disc in the frame. The discs are adapted for rotation around an axis parallel with the spindle axis, the discs being interconnected in rotation by fingers having one end mounted in one of the discs while their other end, which is preferably provided with a resilient sleeve, is received in a matching aperture in the other disc. The fingers extend freely through wide perforations in the casing, which casing is rigidly secured to the spindle and has a radial yarn exit duct communicating with an axial aperture in the spindle, one of the discs being rotated by a radial finger which is rigidly secured to the spindle and connected to the last-mentioned disc.

The connection between the driving finger and the corresponding disc may be provided by a slide block which can rock in the disc around an axis parallel with the disc axis and in which the finger can slide.

Each of the two discs may be mounted, in its respective bearing member, by means of a sealed bearing, and that end of its bore which opens onto its surface bear the disc rigidly connected to the spindle, is provided with sealing means. The annular gap between the spindle and the bore in such disc is connected, at that end of the bore remote from the end just referred to, to an oil supply duct provided in the element which bears the particular disc concerned.

The sealing means of the aforementioned end of the bore of each disc may comprise a washer which is fitted to the spindle and urged against the corresponding sur face of the disc by a spring placed between the washer and the casing rigidly connected to the spindle.

A pulley-driving spindle freely rotatable on the spindle may be provided with a clutch, for instance a cone clutch, which is resiliently urged into its driving position by an engaging spring, while an operable resetting element may be resiliently loaded by a release spring whose action predominates over the action of the engaging spring. A locking system may be provided, adapted to maintain a clutch operating member in the operative position of the clutch, adapted to be acted upon by a declutching element which can be, for instantce, manual or mechanical or electromechanical in operation.

The clutching control element may comprise a cam mounted in the body and bearing thereagainst to release the clutch against the force of its engaging spring.

The invention will be better understood from a study of the following description of the accompanying drawings which illustrate by way and non-limitative example one form of a double-twisting device for textile yarns according to the present invention and in which:

FIG. 1 is a longitudinal sectional view corresponding to line I-I of FIG. 3, of the complete doubletwisting device;

FIG. 2 is a partial sectional view corresponding to line II-II of FIG. 3;

FIG. 3 is a cross-sectional view corresponding to IIIIII of FIG. 2;

FIG. 4 is a sectional view corresponding to line IVIV of FIG. 1;

FIG. 5 is a sectional view corresponding to line VV of FIG. 4;

FIG. 6 is a developed view of the clutch-operating cam;

FIG. 7 is a sectional view corresponding to line VIIVII of FIG. 2; and

FIGS. 8 to are views which show the elements illustrated in FIG. 7 in different positions each offset by 90 from the other.

In the double twisting device for textile yarns illustrated in the drawings, a spindle 2 is mounted, through the agency of a ball bearing 5 and a needle or roller bearing 4, in a frame 1 (see FIG. 1) and the frame 1 is provided with a lug 1a for securing the frame 1 to a spinning or drafting frame or the like. The spindle 2 rotates around an inclined axis XX. The top end of the spindle 2 is provided wit-h an axial passage 3 and bears a box 6 rigidly secured to the spindle 2. The spindle 2 is rotated by a belt (not shown) which runs around a clutched pulley 7 fitted to the bottom end of the spindle 2, by means of a device to be described in greater detail hereinafter. A bobbin of yarn 8 wound on a tube 9 is mounted in a holder mainly formed by a cam 10 carried by a spindle 11 rigidly secured, by a cotter or the like to an outer race of a bearing 12 whose inner race is engaged on the top end of the spindle 2. The spindle 11 has a base 11a rigidly connected by screws 14 to a ring 13 engaged on an outer race of a bearing 15 by way of a bore which has an eccentricity E relatively to the outer cylindrical surface of the ring 13, the same being coaxial of the spindles 11, 2. Mounted in the inner race of the bearing 15, with retention by a cotter or the like, is the hub of a disc 16 which has a bore whose diameter is considerably greater than the outer diameter of the spindle 2 so as to never contact the same. A ring 18 is secured in the top part of the frame 1 by screws 17 and is formed with a bore which has an eccentricity E relatively to the axis of the spindle 2 and which receives an outer race of a ball bearing 19. The inner race of the ball bearing 19 is engaged on the hub of a bottom disc 20 connected for rotation to the top disc 16 by fingers 21 (see also FIG. 3), four of which are provided in this example. The fingers 21 extend freely through matching apertures 22 in the box 6, the bottom end of each finger 21 being embedded in the bottom disc 20 while its top end is provided with a resilient sleeve 31 adapted to slide lengthwise in a corresponding aperture in the top disc 16. The resilient sleeves 31 enable the disc 16 to be assembled rapidly, take up any incorrect alignment, provide a resilient connection between the two discs 16 and 20 and damp polar inertia effects. The hub of the bottom disc 20 is also formed with a bore whose diameter is considerably greater than the diameter of the spindle 2.

Since the two rings 13, 18 have the same eccentricity relatively to the axis XX of the spindle 2, there is an orientation of the rings 13, 18 around such axis at which the eccentric axis of the top disc 16 and the eccentric axis of the bottom disc 20 coincide with one another. The system formed by the two discs 16, 20 and fingers 21 and hereinafter called a lantern can therefore be rotated around an axis Y-Y (FIG. 2) which is parallel with the axis XX and distant therefrom by the eccentricity E, while the spindle 2 and box 6 rotate around the axis XX. The lantern is rotated by the spindle 2 through the system comprising a radial cylindrical finger 23 (FIGS. 2 and 7 10) which is rigidly connected to the spindle 2, the finger 23 is slidable in a diametric aperture of corresponding diameter in a a cylindrical slide block 24 rockable in a cylindrical recess in the disc 20, the axis of such recess being parallel with the axis of the disc 20. Consequently,

the spindle 2, as it rotates, drives the disc 20 via the finger 23 which slides in the slide block 24 while the same oscillates in the disc 20. When the system has performed one revolution, the finger has slid by an amount corresponding to twice the distance E in the slide block 24 and the same has pivoted through an angle a (FIGS. 8 and 10), to each side of a mean position. The drive is therefore continuous and there can be no impacting nor risk of jamming. Inertia effects due to the infinite variation of the ratio between the angle speeds of the spindle 2 and of the lantern, a factor caused by the eccentricity, are absorbed by the resilience of the sleeves 31 on the fingers 21.

This mechanical system for providing a rotating connection between the spindle 2 and the lantern is received in a sealed enclosure formed by a part of the frame 1, the ring 18, the bottom bearing 5, the bearing 19 for the disc 20, and the disc 20. The bearings, which have one face sealedi.e., the bottom face in the case of the bearing 5 and the top face in the case of the bearing 19provide the sealed enclosure for the corresponding part of the enclosure. Radial sealing of the disc 20 is provided by the finger 23 which fills the bore in the slide block 24 and by a plate 25 which closes the assembly aperture for the finger 23 through the spindle 2. The seal between the spindle 2 and the top part of the bore in the disc 20 is provided by a washer 26 which is clamped tightly to the spindle 2 and which is urged resiliently against the top surface of the disc 20 by a spring 27 disposed between the washer 26 and the bottom surface of the box 6. A passage 28 in the frame 1 communicates with the enclosure and is adapted to supply an appropriate lubricant thereto. Similarly, the bearings 12, 15 at the top end of the spindle 2 are bearings whose top face and bottom face respectively are sealed, and a disc 29, which is tightly clamped to the spindle 2, is urged resiliently against the bottom surface of the top disc 16 by means of a spring 30 disposed betwen the disc 29 and the top surface of the box 6. A lubricant can be injected into the resulting enclosure through a passage 32 in the base of the spindle 11.

With regard to lubrication, the clutched pulley 7 is fitted to the bottom end of the spindle 2 by means of two ball bearings 33, 34 which are also of the kind having sealed outer faces. Lubricant can be supplied through a passage 35 to the annular space bounded by the spindle 2, the two bearings 33, 34 and the bore in the pulley 7. The complete device is therefore hermetically sealed so that there can be no loss of lubricant and no entry of dirt into the mechanism.

The base of the can 10 has, near its periphery, an eccentric weight 43 designed, as will be described hereinafter, to form an unbalance adapted in particular conditions to oppose rotation of the bobbin 8. The top end of the pulley 7 has a frustum-shaped female lining 44 forming one of the parts of a cone clutch whose male cone element 45 is slidably mounted, through the agency of a cylindrical core 47, on the spindle 2. The element 45 is urged resiliently towards the lining 44 by a spring 46 bearing against a washer 46a rigidly secured to the spindle 2. The core 45 is also formed with a square aperture matching a corresponding prismatic square cross-section portion 48 of the spindle 2, in order that the cone 45 may be so connected to the spindle 2 as to rotate solidly therewith.

The pulley 7 is shown in its clutched position in FIG. 1. To declutch it, the cone 45 must move upwards to compress the spring 46. To this end, a cylindrical ring 49 is mounted in a matching bore in the bottom part of the frame 1, the bottom edge of the ring 49 having a camming shape corresponding to the developed view shown in FIG. 6. The ring 49 has three identical ramps 49a which bear against three corresponding screws 50 (see FIG. 4). A 60 rotation of the ring 49 in the direction indicated by an arrow f1 lifts the ring 49 from the clutched position into the declutched position in which the cone 45 is out of engagement with the pulley lining 44. In this movement, the ring 49 thrusts against a collar 45:: of the cone 45 through the agency of a wearing thrust Washer 52. The spring 46 is therefore compressed. In addition, as the cone 45 is disengaged from the lining 44 so as to cease to be driven thereby, the rotation of the spindle 2 is retarded by the collar 45a having urged against it the washer 52 carried by the non-rotating ring 49. The spindle 2 therefore stops and the pulley 7 runs idly on the bottom end of the spindle 2.

A spring 61 (see FIG. 5), one end of which is wound on a rod 62 screwed radially into the frame 1 bears at its other end against a roller 60 fitted to a handle 51 rigidly secured to the ring 49 and urges the latter in the direction indicated by the arrow f1 towards the angular position corresponding to declutching of the pulley. The force of the spring 61 can be varied by its top end being introduced into any of a number of apertures in a disc rigidly secured to the rod 62.

The ring 49 can be locked, in the position in which it allows the spring 46 to maintain the clutch engaged, by means of a finger 54 (FIG. 5) engaging in a notch 53 (see also FIG. 6) in the bottom edge of the ring 49. The finger 54 is rigidly connected to a rod 55 which is axially slidable in the frame 1 and which is urged upwardsi.e., towards its locking positionby a spring 56. To declutch the pulley, the rod 55 is lowered, for instance, by a pull on a ring 59 connected to the rod 55 or by energization of a solenoid 58 whose moving member 57 depressed the top end of the rod 55 against the force of the spring 56. The spring 61 then returns the cam 49 into tne clutch release position. To declutch the spindle 2, the handle 51 is moved from position where it is marked 51a into the position wherein it is marked 51 (FIG. 4)i.e., in the direction opposite to the direction indicated by the arrow f1. This operation tightens the spring 61 via the roller 60, then locks the ring 49 by the finger 54 so that the clutch is cocked and locked in the spindle-driving position.

The complete system operates as follows:

Assuming that the pulley 7 is being rotated by a belt and that the cone clutch 44, 45 is in the engaged position, the spindle 2 is rotated around its axis X -X and the finger 23 rotates the lantern 16, 20, 21, 31 around its axis YY. Since the lantern is eccentric of the spindle 2 in the frame and also in the bobbin holder 13, the holder remains stationary. The yarn unwinding from the bobbin 8 enters the top end of the stationary spindle 11 and passes into the axial passage 3 of rotating spindle 2 on wearing elements 36. It then passes to the radial passage 6a of the box 6, to leave by way of a yarn guide 37 and form a balloon 39 around the can 10, the balloon apex being determined by the yarn passing into a ring 40, whence the yarn is taken up by the reducer.

During normal operation when the spindle 2 runs at full speed, the combined effects of centrifugal force, air resistance and the winding pull of the reducer are such that the yarn leaving the yarn guide 37 surrounds but does not touch the can 10. The torque which tends to rotate the bobbin 8 and its holder around the axis of the spindle 2 is the torque produced by friction in the ball bearings 12, 15 due to the weight of the bobbin. This torque is therefore very slight in normal operation.

However, when the spindle starts, before the balloon is formed the yarn is pulled along a path 42 (FIG. 1) and rubs along a generatrix of the can 10. Until centrifugal force disengages the yarn from the can wall, the can tends to rotate and the winding pull tends to tighten the yarn around the can 10, so that the resistance of the yarn to sliding is increased. At starting this force is much greater than the driving force in a steady-state operation. The same thing happens when there is retardation of the unwinding movement of the bobbin 8 during operation. There is then a corresponding increase in the take-up pull 6 and the yarn disengages from the part 41 of the disc 38 and tends to follow the path 42.

The weight 43 at the bottom of the can 10 opposes rotation of the can by the spindle 2. The size of the weight 43 is designed so that the unbalance which it produces balances the driving torque produced by the ball bearings 12, 15.

The action of the weight 43 is inadequate at starting and in the event of disturbances in the unwinding of the bobbin, but the mechanical stabilization keeps the bobbin stationary during such times. In normal operation, however, the unbalance weight 43 alone can maintain the bobbin stable, so that the mechanical eccentric lantern system rotates idly, that is, without exerting a torque on the bobbin holder 13 and the elements connected thereto in order to maintain the bobbin holder stationary, with a consequent saving in driving power and a reduction of wear to a negligible value. In short, stabilization in op eration is provided by a small unbalance weight, while mechanical stabilization is provided as a safety feature at starting, in the event of disturbances during unwinding and at a stoppage of the spindle 2.

Of course the invention is not limited to the embodiment described and shown and can be varied in many ways without for that reason departing from the scope of the accompanying claims.

I claim:

1. A double-twisting device for textile yarns, of the kind wherein an axially bored spindle, having one end rotatably mounted in a frame, carries a bobbin holder, freely rotatably mounted thereon at its opposite end, and a casing which is secured to an intermediate part of the spindle, the casing being provided with a radial yarn passage communicating with the axial bore in the spindle, including means for preventing the bobbin holder from rotating with respect to the frame comprising a relatively small unbalance weight associated with the bobbin holder and rotary mechanical connecting means associated with the bobbin holder and the frame and rotatable about an axis other than the axis of rotation of the spindle,

2. A double-twisting device as claimed in claim 1 wherein the rotary mechanical connecting means comprises a first disc mounted in the bobbin holder for rotation about an axis parallel to but offset from the axis of rotation of the spindle and a second disc mounted in the frame for rotation about the offset axis, both discs surrounding the spindle with free clearance between themselves and the spindle, the discs being interconnectable by at least one finger mounted on one disc and engageable in a matching aperture in the other disc and extending freely through wide perforations in the casing.

3. A double-twisting device as claimed in claim 2 wherein the finger is provided with a resilient sleeve located in the aperture of the other disc.

4. A double-twisting device as claimed in claim 2 wherein the casing is rigidly secured to the spindle and is provided with a radial yarn duct communicating with the axial bore in the spindle, one of the discs being arranged to be rotated by a radial finger, rigidly secured to the spindle and connected to the appropriate disc.

5. A double-twisting device as claimed in claim 4 wherein a slide block is mounted in the appropriate disc for movement therein about an axis parallel to the axis of the disc, the radial finger being slidably engageable in said slide block.

6. A double-twisting device as claimed in claim 2 wherein each of the two discs is mounted, in a respective bearing member, by means of a sealed bearing, the end of its bore which opens onto its surface near the disc rigidly connected to the spindle being provided with sealing means, the annular gap between the spindle and the bore in such disc is connected, at the end of the bore remote from the end just referred to, to an oil supply duct provided in the bearing for the disc concerned.

7. A double-twisting device as claimed in claim 6 wherein the sealing means each comprise a washer, fitted to the spindle and urged against the corresponding surface of the disc by a spring located between the washer and the casing rigidly connected to the spindle.

8. A double-twisting device as claimed in claim 1 wherein a pulley-driven spindle, freely rotatable on the spindle is provided with a clutch which is resiliently urged into its spindle driving position by a spring and with a manually operable resetting element which is resiliently urged by a release spring of greater power than the clutch engaging spring,

9. A double-twisting device as claimed in claim 8 wherein the clutch is a cone clutch.

10. A double-twisting device as claimed in claim 8 including a locking system adapted to maintain an operating member in the operative position of the clutch and actuable by a declutching element.

11. A double-twisting device as claimed in claim 10 wherein the declutching element is manually operable.

12. A double-twisting device as claimed in claim 10 wherein the declutching element is mechanically operable.

13. A double-twisting device as claimed in claim 10 wherein ,the declutching element is electromechanically operable.

14. A double-twisting device as claimed in claim 10 wherein the declutching element comprises a cam mounted in the frame and bearing thercagainst to release the clutch against the force of its engaging spring.

References Cited by the Examiner UNITED STATES PATENTS 2,511,639 6/1950 Koella 5758.78 2,521,601 9/1950 Planet 5758.72 2,541,541 2/1951 Pellat-Finet et al. 5758.72 2,571,854 10/1951 Foster 5758.79 2,576,124 11/1951 Kingsbury 5758.81 X 2,587,758 3/1952 Pellat-Finet et al. 5758.72 2,657,523 11/1953 Kooistra 5788 3,076,305 2/ 1963 Meisser 5788 X 3,167,902 2/1965 Smith et al. 5758.81 X

FRANK I COHEN, Primary Examiner.

D. E. WATKINS, Assistant Examiner. 

1. A DOUBLE-TWISTING DEVICE FOR TEXTILE YARNS, OF THE KIND WHEREIN AN AXIALLY BORED SPINDLE, HAVING ONE END ROTATABLY MOUNTED IN A FRAME, CARRIES A BOBBIN HOLDER, FREELY ROTATABLY MOUNTED THEREON AT ITS OPPOSITE END, AND A CASING WHICH IS SECURED TO AN INTERMEDIATE PART OF THE SPINDLE, THE CASING BEING PROVIDED WITH A RADIAL YARN PASSAGE COMMUNICATING WITH THE AXIAL BORE IN THE SPINDLE, INCLUDING MEANS FOR PREVENTING THE BOBBIN HOLDER FROM ROTATING WITH RESPECT TO THE FRAME COMPRISING A RELATIVELY SMALL UNBALANCE WEIGHT ASSOCIATED WITH THE BOBBIN HOLDER AND ROTARY MECHANICAL CONNECTING MEANS ASSOCIATED WITH THE BOBBIN HOLDER AND THE FRAME AND ROTATABLE ABOUT AN AXIS OTHER THAN THE AXIS OF ROTATION OF THE SPINDLE. 